Feed device for hydraulically operated change-speed gears



April 27, 1948. A. KEGRESSE 0,589

FEED DEVICE FOR HYDRAULICALLY OPERATED CHANGE-SPEED GEARS I Filad April 17, 1939 2 S heets-S heet 1 A.KEGRESSE April 27, 1948. A. KEGREssE 33 FEED DEVICE FOR HYDRAULICALLY OPERATED camen-srnanfanms Filed April 17, 1939 2 Sheets-Sheet 2 Au 0 Z? W];

7 w a A.KEGRESE Patented Apr. 27, 1948 men nsvrcn For. nrnnamcmr orma Amp CHANGE-SPEED cams Adolphe Kgresac, Paris, France Application April 1'2, 1939, Serial No. 268,419 In France April 18, 1938 Section 3, Public Law 890, August 8, 1946 Patent expires April 16, 1958 8 Claims. (01. 192-87) (Granted under the provisions of sec. 14, act

March 2, 1927; 35'! 0. G.

This invention relates to improvements in feed devices for hydraulically operated change-speed gears.

Apparatus is known of the kind comprising a group of hydraulically operated clutches which are combined with gear trains so as to form hydraulically ,controlled change-speed gears, the arrangement being either automatic or manually controlled.

The invention concerns more particularly the provision of members for the admission of fluid. for example lubricating oil, to the clutches, and also the arrangement of the passages for the admission and discharge of the said fluid.

' Experience has shown that in known apparatus of the aforesaid kind as described, for example,

in applicant's U. S.Patents Nos. 2,143,321,

2,163,202, and 2,163,203, the devices corresponding to those provided accdrdlng to the present invention did not ensure in a fully satisfactory manner the functions for which they were intended, either on account of friction or because the arrangement of the passages for the fiow of the liquid and the members controlling said flow were not well provided. The result of these imperfections was irregular, and the excessively slow operation of the apparatus was detrimental to its practical application.

The present invention remedies these disadvantages and comprises improvements in the arrangement of the distribution members and the passages for the flow of the fluid.

According. to the present invention a feed de-,

vice for apparatus of the aforesaid kind wherein n the clutches are arranged in a rotating housing,

embodies a double acting radial valve mounted a three-speed gear. This general arrangement is furthermore known.

In these drawings;

Figure l-is-a vertical section on the line l|- of Figure 2.

Figure 2 is a profile view with a part section on the line 2-'-2 of Figure 1.

Figure 3 is a section on'the line- 1+2 of Figure 2.

Figure 4 is a section ure 2.

Figure 5 shows in section a modification of the control device. a

The group of clutches shown by way of example is of the type having discs compressed by a movable plate to which hydraulic pressure is transmitted through the medium of an annular diaphragm correspondingto each movable plate.

The diaphragms may of course be replaced by V pistons without departing from the invention.

Likewise, the group of clutches may comprise a plurality of discs per speed stage or may be provided for 2 or 4 speeds.

In Figure 1, the driving shaft l carries a plate 2 forming a drum on the face opposed to the shaft I. The drum accommodates the fixed and movable clutch plates and also the diaphragms and return springs. The other face of the plate 2 carries two projections 3 and 4 (Figures '1, 2, 4, 5). The latter, however, without any inconvenience other than the weight, may form a solid continuous ring and thus take the place of a flywheel.

The projection 3 is pierced radially from one end to the other for receiving a valve 5, the lower part 6 whereof engages a likewise radial bore provided in the hub I of the plate 2. a The lower part 8 of the valve 5 has a portion of reduced diameter to provide an annular space 8.

The top of the valve 5 carries a point 9. The

- tion shown in the drawings.

The projection 4 is pierced with two radial openings each of which is provided with a valve i2 having an annular recess I3. Each of said valves is urged towards the periphery by means of a calibrated spring It. The two valves ensure the distribution of the fluid for the second and third speeds.

The arrangement of the clutches themselves and the corresponding gears is known from the' fast with the pinion 25 meshing withthe gear on the line 4-4. of Fig- I wheel 28 also mountedin free-wheel fashion on the driven shaft 22 gives the second speed. The disc 23 is adapted, to be pressed by the movable plate 21,against which the diaphragm 28 bears. The latter is held against one face of the fixed plate 28-, which receives on its other face the diaphragm an controlling the movable plate 8] adapted to press the disc 32 against the inner face of the plate 33, also forming as it were the cover of the drum of plate 2.

The disc 32 drives the hollow shaft 34 fast with the pinion 38 meshing with the gear wheel 88, itself fast with the driven shaft '22 for giving the third speed.

The springs 31 return the movable plates i5,

21 and II to their starting position. The annular struts 38, 38 and 48 maintain the fixed plates in their respective positions and at the same time, provide fluid distributing passages, as will be seen hereinafter. The whole is assembled by the bolts 4 I.

The outer plate 33 has near its centre a helical gear wheel 42 driving the small vertical. shaft 43 actuating the pump 44 situated in the lower part of the casing 48 enclosing the entire mechanism. Said pump 44, immersed in the oil of the casing, forces the latter through the tubular passage 48 as far as a collector 41 forming a bearing, in Figure 1. Obviously, said collector may be independent of the bearing. The shaft of the collector, which in this case is the driving shaft i, is provided with a bore which has a radial portion 48 and an axial portion 48. The latter opens into a radial passage Bil communicating by the orifice 8i provided in the hub 1 of the plate 2 with the groove 8 in the lower part 8 of the valve 8.

Another orifice 82, diametrically opposed to the orifice 8|, relatively to the valve 6, and offset axially relatively to said orifice, communicates with a small annular chamber 53 formed in the plate 2 behind the central portion of the verse passage 88 provided in the projection 4 of" the plate 2, each of the ends of said passage terminating-in the annular space 51 formed in the top of the fluid distributing valves l2.

Each of the valves i2 in the position shown in Figures 1 and 2, that is to say at rest, uncovers an orifice 88 communicating with the exterior, and another orifice 59 diametrically opposed to the orifice 88. Each orifice 59 communicates respectively by a separate passage 60 and 8| (the end of the latter is shown in dotted lines in Figure 1) with a chamber 62, 63 (the latter is shown in dotted lines) provided on the periphery of the fixed plate 29, the chamber 82 opening behind the diaphragm 28 of the second speed and the chamber 82 behind the diaphragm 30 of the third speed.

The passages 88 and Si are also in communication with an opening 84 parallel to the opening 89. The opening 84, in the position in the figures, is covered by the valve l2.

. The periphery of the fixed plate 29 also has two other chambers 85. 88 (Figure 4) almost opposite the chambers 82, 63 and shown in dotted lines in Figure 1, likewise-provided behind the diaphragms 28 and 38 and communicating by the passages 81 and 88 (Figure 4) with the chamber 88 of the projection 3 formed by the top of the valve 8 and a stopper 18 pierced by.

a hole 1i of a smaller diameter than the point 9 of the valvel.

The plate Z'has a third chamber 12 (Figures 1 and 4) situated behind the diaphragm i8 and at the periphery of the latter. Said chamber 12 communicates by the orifice 13 with the chamber 89 of the projection 8.

Figure 5 shows a constructional modification of the centrifugal control of the valve 8-4. A weight 15 is disposed on the end of a lever 18 pivoted to a pin 11 fixed to the plate 2. The lever 18 acts on a collar 18 integral with the valve 8-6. Said collar 18 also bears on the return spring ii of the valve 5-8.

The operation is as follows:

When the engine is started, the pump 44 which rotates with it draws lubricating oil and forces it through the passage 48 to the collector 41. Through the passages 48, 48 and 58 and the orifice 5i, the oil enters the annular space 8.

If the engine speed is low, the valve 88 remains in the position of Figure 1 and the oil does not pass beyond the space 8. there being no .outlet open. On the contrary, as soon as the engine speed increases, the valve 8-6 loaded by the weight i8 compresses the spring ii under the action of the centrifugal force and .thus moves towards the periphery, uncovering the orifice 82 which it puts into communication by the space 8 with the orifice 5i connected to the collector 41 and consequently to the pump 44.

The stroke of the valve 8-8 is limited towards the periphery by the point 9 which obstructs the hole 1| of the stopper 10. The oil passes through the orifice 52 and the chamber 53 bedisc i8 against one of the faces of the fixed plate l1, and thus causing the first speed train to be driven. The oil compressed behind the first-speed diaphragm i6 seeks to escape throughthe chamber 12, orifice 13 and chamber 89 but does not find there-any outlet as long' as the centrifugal force keeps the point 9 of the valve 5 applied against the stopper 10, and also, through the chamber 54 and the passages 65 and 56 which leadit into the small chamber 81 provided-in the outer part of the valve 12 of the second and third speeds.

These valves i2, the weight of which balances, in respect of the centrifugal force, that of the column of oil feeding them, are known from the specifications of applicant's previously mentioned U. S. Patents Nos. 2,143,321 and 2,163,202. They are held on their seats respectively by the springs i4 ofdifl'erent graded tensions, the spring of the second-speed valve being distinctly weaker than that of the third-speed valve. It follows that as soon as the oil pressure behind the diaphragm it has attained a sufllcient value, the secondspeed valve i2 opens and allows the oil under pressure to pass through the conduits 64, 88 and chamber 82 and distend the second-speed diaphragm 28 which, by moving the plate 21 causes it to apply and press the disc 23 against the other face of the fixed plate i1. The second speed then becomes operative.

The oil pressure then continues to increase.

' since no outlet is offered to it, and attains a force greater than that of the spring 14 acting on the third-speed valve i2, The latter opens in its turn, under the action of the pressure, for directing the fluid through the passages ii to the QAAOJBO sure drops sufficiently, the valves I! put the chambers formed behind the diaphragms 28 and 30 into communication with the exterior via the passages 80 and 8|, groove l3 and discharge orifice 88.

If, when the vehicle is running normally, it is stopped very abruptly by a sudden application'of the brakes, itwill be appreciated that the weight ill, the effect of the centrifugal force on which isgreatly reduced on account of the sudden slowing down, is returned rapidly towards the centre under the action of the spring. I I, carrying with it the valve 5-8. The orifice H is immediately uncovered and permits the centrifugal discharge of the oil contained behind the diaphragms, through the medium of the conduit 13 for the first speed, and that of the passages 81-88 for the second and third speeds. At the same time as the point 9 uncovers the orifice II, the valve 5-6 shuts off the admission of oil through the orifice 52, since it then re-assumes the position shown in Figure 1. At the same instant, the valves 12 themselves become operative for putting into communication with the exterior the chambers formed behind the diaphragms of the second and third speeds, as in the above-mentioned case of a simple drop in pressure. It will be seen therefore that the discharge of the oil from behind the diaphragm is practically instantaneous, since it may be eifected at several points simultaneously. y The advantages of the device according to the invention relatively to the known constructions reside in the following points:

More reliable operation of the fluid admission valve 5-8, due to the weight ill, or to the leverweight device of Figure 5, which renders it less sensitive to passive resistances: such as friction,

rupture of the oil film or expansions.

Double function of the valve 8-8 which regulates the admission of fluid and its discharge in v a simple manner.

Without detriment to the discharge of the fluid which always takes place under the effect of the centrifugal force, a quicker start is obtained, due to. the centre filling of the first speed diaphragm, said filling being controlled directly by the lower part 8 of the general fluid admission valves 5, said part being very close to the first speed diaphragm, while retaining the peripheral discharge. In fact, if the engine is running slow, the fluid filling the'space 8 is ready to flow very rapidly, at the slightest acceleration of engine, behind the the first-speed diaphragm l8 under the twofold action of the pressure and centrifugal force. The

path which it has to fiow through being very limited, it will be appreciated that the filling of the chamber behind the first-speed diaphragm will be almost instantaneous, withouton that account impairing the discharge of said chamber when necessary, since such discharge will be effected through an opposite orifice situated on the periphery, that is to say under action of the centrifugal force. This arrangement permits instantaneous starting. As the fluid has no distance to travel, its action is immediate which was not the case with the known'devices.

I claim:

1. In a feed device for clutches with hydraulically compressed discs wherein the clutches are arranged in'a rotating housing, a double-actin radial valve mounted on the rotating clutch hous- 8. th'e part thereof adjacent the axis of thehousing controlling the admission of fluid to the device from the feed system, the part of said valve adjacent the periphery of the housing controlling the discharge of said fluid, a pivoted lever engaging said valve for actuating the latter, and a centrifugal weight fixed to the end of the lever acting on said valve.

2. In a feed device for clutches with hydraulically compressed discs wherein the clutches are arranged in a rotating housing, a rotary plate, a first-speed-stage diaphragm carried by said plate, said plate having an admission valvechamber adjacent the axis thereof and a discharge valve chamber adjacent the periphery thereof, and a centrifugally responsive double-acting radial valve common to both chambers, said admission valve chamber having a port placing saidchamber in communication with saiddiaphragm when uncovered by said valve.

3. In a feed device for clutches with hydraulically compressed discs'wherein the clutches are arranged in a rotating housing, a rotary plate, a

first-speed-stage diaphragm carried by said plate. said plate having an admission'valve chamber adjacent the axis thereof and a discharge valve chamber adjacent the periphery thereof, and a centrifug-ally responsive double-acting radial valve common to both chambers, said admission valve chamber having a port placing said chamber in communication with said diaphragm when uncovered by said valve and said discharge valve chamber having a port communicating with said diaphragm and adapted to be covered by said centrifugally responsive double-acting radial valve common to both chambers, said discharge valve chamber having a port communicating with said diaphragm and adapted to be covered by said valve when displaced radially outward by centrifugal force and uncovered to relieve fluid pressure in said diaphragm upon the reduction of speed of rotation of said plate.

5. In a feed device for clutches with hydraulically compressed discs wherein the clutches are arranged in arotating housing, a rotary plate, a first-speed-stage diaphragm carried by said plate, said plate having an admission valve chamber adjacent the axis thereof and a discharge valve chamber adjacent the periphery thereof, a centrifugally responsive double-acting radial valve common to both chambers, said discharge valve chamber having a port communicating with said diaphragm and an outlet orifice, a pointed member carried by said valve for closing said oriflce lically compressed discs whereinthe clutches are arranged in a rotating housing, a rotary plate, a iirst-speed-stage diaphragm carried by said sively Placing said other speed-sta8e dim m plate, said plate having an admission valve chamber adjacent the axis thereof and a discharge valve chamber adjacent the periphery thereof, a centriiugaily responsive double-acting radial valve common to both chambers, said discharge valve chamber having a port communicating with said diaphragm and adapted to be covered by said valve when displaced radially outward by centrifugal force and uncovered to relieve fluid pressure in said diaphragm upon the reduction of speed of rotation of said plate, a plurality of other speed-stage diaphragms, said plate having other valve chambers, one for each other speed-stage diaphragm, communication ducts extending between said other speed-stage diaphragms and the corresponding va-lve chambers, a communication duct extending from said first-speed-stage diaphragm to said other valve chambers, and valves in said other valve chamber responsive to successive pressure increases for successively placing said other speed-stage diaphragms in communication with said firstspeed-stage diaphragm. 7. In a feed device for clutches with hydraulically compressed discs wherein the clutches are arranged in a rotating housing, a rotary plate, a flrst-speed-stage diaphragm carried by said plate, said plate having an admission valve chamber adjacent the axis thereof and a discharge valve chamber adjacent the periphery thereof, a centrii'ugally responsive double-acting radial valve common to both chambers, said admission valve chamber having a port placing said chamber in communication with said diaphragm when uncovered by said valve, said discharge valve chamber having a port communicating with said diaphragm and adapted to be covered by said valve when displaced radially outward by centrifugal force and uncovered to relieve fluid pressure in said diaphragm upon the reduction of speed of rotation of said plate, a plurality of other speed-stage diaphragms, said plate having in communication with said iirst-speed-stage dia- Phragm.

8. In a feed device for clutches with hydraulically compressed discs wherein the clutches are arranged in a rotating housing, a rotary plate, a first-speed-stage diaphragm carried by said plate, said plate having an admission valve chamber adjacent the axis thereof and a discharge valve chamber adjacent the periphery thereof, a centrifugally' responsive double-acting radial valve common to both chambers, said discharge valve chamber having a port communicating with said diaphragm and adapted to be covered by-said valve when displaced radially outward by centrifugal force and uncovered to relieve fluid pressure in said diaphragm upon the reduction of speed 01. rotation of said plate, a plurality 01'. other speed-stage diaphragms, said plate having other valve chambers, one for each other speed-stage diaphragm, communication. ducts extending between said other speed-stage diaphragms and the corresponding valve chambers,

a communication duct extending from said firstspeed-stage diaphragm to said other valve chambers, valves in said other valve chamber responsive to successive pressure increases for sueces'sively placing said other speed-stage diaphragms in communication with said first-speedstage diaphragm, and conduits placing said other speed-stage diaphragms in communication with said discharge ,valve chamber and adapted to be closed oil when said discharge valve is in its radial outer position.

ADOLPHE KEGRESSE,

REFERENCES CITED The following references are of record in the file of this patent:

Netherlands Oct. 15 1937 

